FCVHRM,frq,k,hrq,frc,dmp,selForced vibration under a harmonic force with damping

frq natural vibration
frequency in KHzk spring constant
in N/mhrq frequency of the
driving force in KHzfrc
amplitude of the driving force in µNdmp damping ratiosel number denoting the
selected result.
Use 1 for amplitude of vibration, 2 for phase lag and 3 for resonance frequency

Notes

The natural frequency of vibration of structures estimated under Vibration >
Free vibration assumes that damping is not present and no external force is
acting on the structure. In reality, some form of
damping and external forces are present in many MEMS devices. In many cases
MEMS sensors will be subjected to time varying forces with constant
amplitudes like electrostatic force and its response
to such external loads needs to be understood. When a spring mass system
representing the MEMS device is subjected to a harmonic excitation as shown,
the applied force varies harmonically with amplitude 'frc' and radial
frequency 'wf'. Based on the initial conditions including displacement and
velocity of the mass, it will undergo a transient response immediately after
it starts to vibrate. But as time becomes large, it assumes a steady state
response which will be independent of the initial conditions. Only steady
state vibrations are examined here and assumes that time is large so that
transient response can be neglected.

This design interface can be used to estimate the resonance frequency,
amplitude of vibration and
phase lag. The frequency of forced harmonic vibration will be the same as
forcing frequency. The resonance frequency is dependent on the natural
vibration frequency and damping. When the damping is very small, the resonance
frequency is nearly equal to the natural vibration frequency. The vibration
amplitude is strongly dependent on damping, the excitation frequency and the
properties of the spring mass system. The vibration amplitude is highest when
the driving frequency is near the resonance frequency and should be avoided in
most cases. When the damping ratio is equal to 0.7, the peak in the amplitude
frequency curve nearly disappears and that allows a wide range of excitation
frequency to be applied which will not make any change to the vibration
amplitude. Hence a damping ratio of 0.7 is known to give a wide bandwidth and
is often referred to as the optimum damping condition.

The free vibration frequency is as estimated for the various structures under
Vibration > Free vibration. If the damping ratio for air damping is not
available it could be estimated using the design forms under Vibration >
Damping for a given air gap distance. If spring constant is not known it
can be calculated under Mechanics > Structures.

The resonance frequency is estimated for
the under damped case (dmp < 0.7) only. There is a phase lag in the
vibration of the system with respect to the driving force depending on the
damping ratio, the excitation frequency and natural frequency of vibration. If the amplitude of vibration
is known, dividing it by the static displacement of the mass which is frc/k
will give the relative amplitude.

The plot shows relative amplitude of vibration of the
system for a range of driving frequency above and below the natural frequency
of the system for the given damping ratio. When the damping is slight (dmp <
0.7), the maximum relative amplitude obtained from the curve is equal to the
Quality factor or Q-factor of the system. This maximum amplitude happens also
at the resonant frequency. Using the cross hair tool, the resonant frequency,
the Q factor and the amplitude of vibration of the system can be estimated
from the graph.

Assumptions

-Only steady state response is considered.
-For air damping, the damping ratio should correspond to that particular mode of
vibration.